Pump



Nov. 14,1944.

7 H. E. ADAMS PUMP Filed Au 2, 1940 6 Sheets-Sheet l Inven tor {119F010 EflDflM, 4. Q

, Q ttorneys Nov. 14, 1944.

H. E. ADAMS Filed Aug. 2, 1940 4 6 Sheets-Sheet 2 inventor f/FPOL'O E. flax/v.5,

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Nov. 14, 1944. ADAMS 2,362,954

PUMP

Filed Aug. 2, 1940 '6 Shee ts-Sheet s .a a. w

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' Nov. 14, 1944.

H. E. ADAMS PUMP 6 Sheets-Sheet 5 Filed Aug. 2, 1940 Nov 14, 1944- H. E. ADAMS 6 Sheets-Sheet 6 Filed Aug. 2, 1940 liquids beins Patented Nov, 14, 1944 UNITED STATES:

Harold E. Adams, South Norwalk, Conru, assignor to Nash End eering'Company, South Nor-walk,

Conm, a corporation of Connecticut Application August z, 1040, Serial No. tract:

22 Claimsusal D p liquids, and liquid piston means are provided for the pumping of. gases, in conjunction with the pumpedby the centrifugal means. It has been the practice in the past to use entirely separate pumps for handling liquids and gases, these pumps not necessarily operating at the same rotativespeed. A later improvement was made so that .both pumping means could operate at the same rotative speed and the two units could be coupled together and driven by a' common driver. Subsequently, in order to reduce costs and conserve space for the pumping equipment, manufacturing practice brought about a change in the design of pump casings and-a shortening of, the drive shafts in order to move the several pumping units closer together. This has been favorably accepted in the trade, and has resulted in the use of a common casing, as well as a common drive shaft for the multiple units, the respective impellers, however, being separated by partitions in the casings, dividing same into independent pump chambers for each unit.

The patented art is replete with typical instances of past and present designs of pump caslugs, and present day practice utilizes very com- I the previous practice consisted in employment of separate, independent casings spaced from'each other, even though a common have been used.

It is a primary object of the present invention drive shaft may to carry this combination still further in a novel,

yet very successful, arrangement that combines the liquid and gas rotating members into a single so unit as well as utilizing a single pump casing and com ent, thus reducing the size and'cost of the unit.

Another'object is to form the partition wall between the pump units as a part of a combined so pact multiple unit pumps having a centrifugal I impeller member, one side of pump gases and the other side of which handles liquids.

' Another feature of the present invention is to '5 devise a construction using a combination liquid and gas'pump reduced to a single unit.

Another advantage of the present invention residesin the design of the pump casing and pumping member to effect a novel seal between the pump chambers at points remote from the drive shaft. v

A still further is ture of the present invention is toprovide for increased efflciency through the reduction of hydraulic losses in the overall unit and at the same time produce a very material reduction in manufacturing costs.

To the attainment of the foregoing and other objects which will hereinafter appear as the de scription proceeds, reference may be made tothe accompanying drawings, wherein: I

Figure 1 is a sectional elevation through a pump assembly, showing an adaptation of the present invention and is taken substantially on the line i-l of Figures 2 and 3.

Figure 2 is a sectional view through the pump assembly taken substantially on the line 2-2 of Figure 1. 1

Figure 3 is a assembly taken Figure 1.

Figure 4 is a part sectional view showinga seal sectional view through the pump substantially on the line 3-3 of arrangement modified with respect to Figure 1' and using a relief valve.

Figure 5 is a part sectional view showing a seal arrangement modified with respect to Figures 1 and 4 using an orifice in the pipe line.

Figure 6 is one face view of the pumping ment shown in Figure '7.

Figure 'l is a diametric. section through a'form of pumping element or rotor as adapted for the present invention.

ele-

gure 8 is the other face view of the pumping element'or rotorshown in Figure '7.

Figure 9 is one'face view of the liquid pumping element shown in Figure 10.

Figure 10 is a diametric section through a form.

of liquid pumping practice of in the modification shown in Figure 13.

Figure 11 is a diametric section through a form of gas pumping element as used in accepted practice of' multiple pump assembly, and as used in the modification shown in Figure 13.

element as used in accepted which functions to multiple pump assembly, and as used Figure 12 is one face view of elementgshown in Figure 11.

Figure 13 is a sectional view through a multiple pump assembly illustrating a modification of accepted practice of constructing pump organizations, in accordance with the present invention.

Figure 14 is a sectional view of a combined impulse and liquid ring pump taken on the line |4-l4 of Figure 15, and

' Figure 15 is a sectional viewthereof taken on the line |l5 of Figure 14.

Referring now, more specifically to the drawings, wherein like reference numerals indicate like parts, H indicates a pump housing of a particular type used with the liquid pumping section selected for the purpose of illustrating the invention. H indicates the housing for the gas pumpin section. S indicates a separating tank of the pump assembly wherein particles of liquid are removed from the gas discharged from the gas pump.

M indicates a prime mover in the form of an electric motor, mounted on the pump housing, as shown in Figure 1, and this motor drives the rotary drive shaft II. In the preferred form of the invention, the shaft I1, as illustrated, is disposed on a horizontal axis, but it is to be understood that the principle of the invention 'will function as well with the shaft disposed on a vertical axis, or any angular disposition between the vertical or horizontal axis, should the requirement of any such unusual installation be specified.

In the form-of the housing H selected toillustrate one adaptation of the invention, the volute portion 18 of the pump casing H. is preferably cast or molded integral with one of the partition walls I! to define a pumping compartment. However, it is to be understood that the present invention is in no way limited to this particular construction, for the pump compartment may be made separate from the housing H, in which event it would be self-supporting; or it may be made separate and attached to any device for which its peculiar function of pumping liquid and gas simultaneously is adapted.

In all forms of the present invention, the rotating pumping member that carries the pump elements, divides the compartment. formed by the assembled parts of the housing H--H into separate pump chambers. Each chamber has a set of passages including an inlet and an outlet passage. In Figure 1, the parts of the pump casing or housing H-H in the assembled relation,'form the pumping compartments 2| and 20. These compartments are divided by the rotating pumping member P. The rotating pumping member P consists of a central supporting disc 42, on one face of which are carried the centrifugal liquid pump elements 45, and the elements 45 which function as the liquid ring gas pump are carried by the Opposite side of the disc 42, thereby creating a, unitary or combination impeller-rotor.

The centrifugal pump elements operate in the pump chamber 2|, and in the other chamber 20 the liquid ring gas pump elements operate, and of course, each chamber is provided with an inlet and an outlet passage.

In the form of the pump casing H shown in Figure 1 of the drawings, the volute portion or head of the casing is indicated at 18. Around the'inside of the head part I 8, near the periphthe gas pumpin ery, is the volute passage or compartment 2| nut 44.

which is the discharge for the centrifugal liquid pump. The liquid ring pump housing H is secured at its marginal portion by the bolts 22 in depending relation to the volute or head I8.

The pumping member P shown in detail in Figures 1, 6, '7 and 8 of the drawings. is a combined impeller-rotor and comprises a, central supporting disc 42 which carries on one face the impeller elements 45 for the centrifugal pump, while on the opposite face are carried the rotor elements or vanes 46 which constitute the rotor of the liquid ring type of pump.

The center of the disc 42 merges with an outstanding hub 43 keyed to the drive shaft ll, which is driven by the motor M, and the disc is secured to the drive shaft by means of the The impeller blades '45 forming the pumping elements for the centrifugal liquid pump and the vanes 48 for the liquid ring pump are preferably cast or molded integral with the disc 42.

On the face of the disc remote from the blades 45 is a ring-like lip 41, the outer edge of which conforms in shape to a lip 50 on the housing 1-1 but there is a slight clearance between the two surfaces to form a liquid seal 25.

At each end,of the blades 48 are concentric ring-like depending lips 48. The outer face of the lips 48 conform in shape with confronting lips 5| on the side walls of lobe chamber 28, but there is a tolerable clearance between these confronting faces to form liquid seals 23 and 24 preventing leakage of any gas from the gas pump. The vanes 48 terminate short of the center of the disc 42 to form an inverted cup-like cavity 52 mating with the frusto-conical port member 52.

The passages 53 of the centrifugal impeller of the pumping member P are confined between the shroud plate 54 and the confronting face of the disc 42, and these passages are bounded laterally by adjacent blades 45.

The buckets or displacement chambers 55 for the rotor of the liquid ring part of the pumping member P are confined between the shroud 58 and the confronting face of the disc 42 and they are bounded laterally by the adjacent vanes 48. The shrouds 54 and 58 are round plates that may be secured to the blades or cast integrally with the pumping element to the lower edges of the vanes. In fact, with some constructions the shrouds may be omitted, the present showing being of course, merely illustrative.

The principle of operation of a liquid ring gas pump is well known inthe art-and consists of using a liquid piston in the outer portions of the buckets or displacement chambers 55. As the member P rotates, the liquid piston moves out and in of the buckets by centrifugal force and reaction in the lobe passage 20 and the land 51, Figure 2; whereby gas in the inner ends of the buckets is withdrawn from the inlet passage 4|, through the inlet port 58 in the port member 52, and is compressed in chambers 55 and expelled through the outlet port 59, in the member 52 from where it is discharged into the outlet passage 88. Gas enters the inlet passage 4| through a pipe 38, and is discharged through the outlet passage 88 and pipe 8| to separator 32 wherein any sealing liquid used in the liquid ring pump, which may have become entrained in the discharging gas, is separated and returned to the system through theball float valve 34, or the connections ll-fl, hereinafter described. The

. sponding multiple sets out that the central driving disc insuflicient amount of in the breakdown of its per-- asoaoss 3 gas is discharged from the separator through the pump or compressor. This latter condition, howpipe 02. ever, is not arbitrary.

In the illustrative embodiments herein, a gas pump having a single eccentric lobe or displacelargely for simplicity.

ment chamber is shown, The liquid piston pump,however, referred to is notrestricted to this type but may include pumps having'several eccentric lobes and with correof inlet and outlet ports. The construction of the liquid pump may also vary considerably from that shown and may be any of the numerous designs in use. For example, Figure 1 illustrates a pump of type, while Figures 14 and 15 show a pump of the impulse type, exemplified ,bythe patent to Jennings 2,073,014. 1

Referring now to the unitary construction of this invention as shown in Figure 42 in effect replaces the conventional stationary side wall or partition 0f a liquid pump casing, which may'also forni the stationary side-wall of a gas pump casing, while at -the-same time forming a common rotating disc in place of the usual impeller shroud 65 of the liquid pump and 18 of the gas pump (Figures 10, i1 and 13). A material increase in emciency, due to reduced friction losses, effected by the impeller-rotor construction of Figure 1, for friction losses between the rotating liquid in the gas pump with its side wall have been entirely eliminated. The friction losses between the rotating liquid in a liquid pump casing with its side wall are materially reduced and in addition to this, the friction loss of a rotating shroud such as portion of the friction loss of the rotating shroud es of the liquid pump, are entirely eliminated. It is thus evident that the combining of the gas and liquid impellers in one element effects a material increase in efiiciency as well as the reduc-* tion of space and costs.

the centrifugal 1, it is pointed- 18 of the gas pump,'and a large either as a vacuum pump,

' operate as a gas compressor by nular chamber 26 and is thus This innovation of combining such dissimilar by various sealing arrangements, to be described that enable the gas pump and the liquid pump to operate satisfactorllyin such close relationship.

The performance of liquid pumps, as is well known in the art, is susceptible to inefficiency caused by traces of gas being mixed with the liquid, such a mixture resulting in the breaking down of the centrifugal action, due to the pres ence of lighter gas bubbles. On the other hand, a gas compressor is very sensitive to the quantityof liquid seal induced into its chambers.

seal or an excess. amount of seal may result formance. Some of the features forminga part of this invention for the segregation and control of these two dissimilar fiuids may be described as follows: I

As a general thing it is assumed that under normal operating conditions, the liquid pump is assured of a supply of liquid at the inlet to this pump, the presence of this liquid being assured, if necessary, by automatic fioatcontrol of the discharge, or a pressure relief valve located in the discharge, or other similar means where there is a possibility of the suction side being uncovered due to a limited supply of liquid. It is also elements inone rotating member is made possible tween the lobe over years of service.

any losses in lobe chamber 20 may vary over It will be note'd,'therefore, that if only one The gas pump or compressor may operate where its normal discharge pressure would be atmospheric, or it may compressor over any usual pressure range compatible with its design and proportions.

It is furthermore assumed that the gas pump or compressor is sealed with the same type of liquid that is being pumped by the liquid pump itself, in factprimary seals will beeflected by liquid from the centrifugal side, sures of the centrifugalpump. Make-up sealing liquid can be introduced into the gas pump or any of the conventionalmethods now used. In the drawings one method is illustrated as at 8|, of introducing auxiliary or makeup sealing liquid into the inlet of the gas pump for the purpose of sealing various points of clearance within the gas pump and compensating for the original seal. It will be noted that an annular chamber 26 is formed between the two sealing surfaces 24 and 2!. An orifice 21 communicates between the anthe outer chamber 28, this chamber being an irregular space formed be tween the outer wall 29 of the liquid ring pump housing and the enclosing wall 30.

If the pressure in the annular chamber 26 is materially higher than the discharge pressure of the liquid ring pump, it will force an excessive amount of sealing liquid through the sealing surfaces at 24 and overload the liquid ring pump end with an unnecessary amount of sealing liquid, with resultant increased load and lowered efficiency of this unit.

Provision is made by this invention to limit the formation of excessive pressure about the sealing surfaces 24. The impeller-rotor combination may be made with impeller diameters and rotor diameters of widely varying values, according to the particular service to which they are applied. Theliquid ring pump rotor diameter is varied to suit the rotational speed of the driving motor to give the required peripheral velocity.to the outer diameter of this rotor. The required peripheral speed of the liquid impeller, however, may vary widely according to the pressure at which it.may be designed to deliver the liquid. This, therefore, requires a specific diameter of liquid impeller for each designed pressure service.

It may be seen that the designed pressure difference between the volute passage 2| and the a wide range.

sealing surface were provided,- such as 24 bechamber 20 and volute passage 2|, there would be a wide variation in the requirements for maintaining tightness at this point. A suificiently tight joint here might be provided but it might conceivably be difllcult to maintain This seal could be maintained by the use of a replaceable'seal but a better method of a controlling the pressure difference across the seal 2 is indicated. 7

The primary sealin rings or lips with sealing surfaces at 25, have been supplied, which take care of the initial pressure passage 2| to the annular ring chamber 26. The relief orifice 21 relieves the leakage that thus enters the annular chamber 26, draining this excess leakage into the chamber 28. The sealing liquid entering chamber 28 is drained of! through other the inlet of the gas 15 control meansas hereinafter described, the methunder the presi drop from the volute sealing at the surface 24.

d being to regulate the pressure in chamber 28 such that a fairly constant pressure is maintained in the annular chamber 28 and hence on the sealing surfaces at 28, of the liquid ring pump rotor. For the regulation of pressures in the intermediate chamber 28, several alternative means may be employed, according to the particular structures involved, illustrations of several alternatives being shown in Figures 1, 4, 5, 14 and 15.

In the method of control 01 pressure in chamber 28, Figure 1, there is provided a connection 3| in communication with'the separator chamber 82 by a connection 88. The separator chamber 32 during the normal operation of the pump is at the discharge pressure of the gas compressor or vacuum pump and is fairly constantly maintained at this pressure.

It will thus be seen that with the inter-connection of chambers 28 and 82, the liquid relieved from the annular space 28 through the orifice 21 will be bled off into the chamber 82 and essentially keep chamber 28 slightly above the discharge pressure of the gas compressor. The excess leakage liquid bled oil by orifice 21. after delivery into the separator 32 will be returned through the float valve 84 back into the inlet side of the structure at 85. By these means a fairly constant desired pressure, slightly in excess of the gas compressor discharge, will be maintained in the annular space 28 and the sealing surfaces 28.

Should the discharge pressure of the liquid pump drop below that of the gas pump, the pressure in chamber 28 will not drop materially below the gas pump discharge pressure, due to the presence ofthe liquid at discharge pressure in chamber 28, thus maintaining the necessary liquid seal at 24.

Stated somewhat in other language, the liquid in the chamber between the liquid ring impeller and the centrifugal impeller is maintained at a pressure. approximately equal to the discharge pressure of the liquid ring pump for the purpose 'of promoting and maintaining a seal between the clearance spaces of the liquid ring impeller, as well as between the liquid ring and centrifugal pumping units. In this connection, the seal, maintained by the discharge pressure, is somewhat similar to the principles described in the patent to Adams, No. 2,195,395.

Additional means, embodying these principles, are provided to ensure a liquid seal at sealing surfaces 28 and 28, by the addition of an orifice 31 communicating with these sealing surfaces 23 and 88 from chamber 28. The orifice 31 is provided to limit. the seal supply to the above sealing surfaces to the desired amount.

A variation of the above control of pressures in chamber 28 is accomplished by bleeding off the leakage into this'chamber through pipe 3| to the inlet side of the liquid pump as at 85, as shown in Figure 5. In this case a suitably sized orifice 88 would be provided to prevent the lowering of the pressure in 28 from approaching that of the inlet side of the compressor, as this compiete lowering of pressure would be detrimental, in that it might not maintain suflicient seal pressure in the annular chamber 28 for the proper This latter connection at 38 would be resorted to in cases of combinations using impellers for extremely high delivery pressure in the volute passage 2| where greater leakagemight be expected and where such leakage might be greater. than float control valve 84.

the capacity of the Another alternate method of controlling the lieu of the free orifice 21, or to relieve the chamber 28 through pipe 3|. The pressure maintained in chamber 28 and consequently chamber 28 would be regulated by the relieving action of the spring controlled relief valve 40, The relief valve 48 shown is atypical automobile tire valve and such a relief valve may be used on very small D P The invention is not limited, however, to this particular type of valve as larger valves would be required on larger pumps. Any relief valve arrangement tending to maintain a substantially constant pressure or a substantial pressure difference in chamber 28 by bleeding off" liquid through the relief valve and pipe 8l to the low pressure side of the pump chamber "18, as at connection 88, can be used.

When using such a relief valve, the orifice 88 in the pipe 3| as shown in Figure 4 would not be used.

In Figures 9 and 10 there is illustrated a centrifugal impeller for a liquid pump as used in accepted practice of constructing multiple pump assemblies, while in Figures 11 and 12 is shown a rotor for aliquld ring pump assembly, as similarly used. Accepted practice, as heretofore.

- pactness, saving in manufacturing costs of the impeller elements and associated structures, will be at once apparent.

However, under some circumstances, it may be desirable to utilize the principles of this invention with separate impellers, in structures similar to present accepted practices.

Figure 13 illustrates an adaptation of a pump organization as used in accepted practice of multiple pump design, but wherein the principles of the present invention are employed. Instead of using a composite impeller wherein the liquid pump, and gas pump impellers are formed as a unitary construction with the equivalent of a partition well built into the dual impeller, the separated impeller elements shown in. Figures 9 to 12 are employed, but the customary partition between the pump chambers is removed. This requires some means of sealing the gas pump chamber from the liquid pump chamber.

In this embodiment the liquid pump impeller 88 is constructed with a circumferential lip 88 outstanding from the driving disc 88. The outer ilar to head section 1-! tion shown in Figure 1.

The rotor 88 is an independent member mounted on the end of the thus seen that there is, in eifect a separate common drive shaft. It is liquid impeller and casing and a separate gas impeller and casing built in unitary construction,

the impellers driven by a common drive shaft.

The chamber 28 corresponds the chamber 28 of v similarly corresponds ure 1, although different. Between the fice 21, and extending from the a passage 31 which cooperative with the sealing Figure 1. and'the chamber to the chamber 280i Figobviously the proportions are 28 and 28 is the restricted orifice 21 corresponding to orichambers corresponds to surfaces 28 and 88.

function to 28 chamber 28 is the orifice 81 In this form, one shroud of the gas pump rotor will be sealed, as indicated at manner comparable 28 and 88 in a to seals 28 and 38 of Figure 1,

and the other shroud will be sealed as indicated at H. in a manner equivalent to the seal 24, and

the chambers 28 and sages and orifices tain the proper pressures 28 together with the pas- 21 and 81 cooperate to mainat the sealing surfaces,

just as described in connection with Figure 1.

The connections (not shown), as well as same as in Figure 1.

8| and 88 from the separator the connection 88 are the It might .be noted. in the description of this figure, that where the elements are identical with those shown in other figures, the same numerals have been used, but where the elements are structurally somewhat different, even though equivalent. primed or wholly new numerals have been used.

Obviously, various sealing between the modifications in the mode of two pump casings may be provided, within the scope of this invention, ex-

amples of such 4 and 5, previously described.

Referring now to Figures seen that the invention combination of 'a centrifugal gas pump of the liquid ring forms of liquid pump impulse or scraper" type may diing liquids at high pressures.

variations being found in Figures in other words, the impulse type of impeller will develop much higher discharge pressures for a given diameter and speed than a centrifugal pump oi the same diameter and application in Figures some usages, such small quantities of against high of usage for of the invention are The gas pump portion of the speed, and the.

of the invention to a pump as shown 14 and 15 is particularly desirable in as heating systems, where liquids must be delivered pressures, as compared with the type which the previously described forms readily adaptable.

unit shown in this embodiment is identical with that disclosed in Figure 1, and no is necessary, the same reference inc. been used. The

of this unit further description thereof numerals havgeneral construction of the is substantially Jennings patent, No. 2,073,- in this instance the impeller has been combined unitarily with the rotor of the gas pump, and

the central driving disk portion of t e dual impeller made to function, by cooperation of the sealing means provided. as a movable partition wall, just as in the earlier forms of the invention? described Since the mode of operation of the liquid'pump portion of the unit is well known,

thoroughly dewith 14 and 15, it' will be is not confined to the liquid pump with a type, but that other such as a pump of the be used, for hanadjacent the'operating buckets or on the impeller or V The inlet connection 81 communicates through 1 immediately chambers 8| a channel 88 with an opening formed by impulse blades 82 rotor 88. The buckets-are enclosed at their sides by .the central driving disk I! which forms a commonwall between the rotor of the gas pump, and the impeller of the liquid pump, and the shroud N.

In operation, the liquid is carried around from the inlet opening 88 through the volute chamber 88, under the blades 82, and where, by this action; the pressure on the liquid is built up to that of the desired discharge. The liquid is ejected from the impulse wheel or impeller 88 into the passage 88', from whence it passes into the discharge chamber 81, being finally discharged at the outlet 88.

In order to apply the principles of the present invention to a as to the combination of such a pump'with a gas pump rotor, seals are provided at the points 88 and 88, thus makingit possible to retain the liquid being pumped, at high pressure between the impeller wheel 93 and the volute 88. The

seals areprovided by cooperating sealing surcal with thatshown in Figure 1. The additional seal 88, in cooperation with the seal 88, represents an improvement in impulse type pumps, as conventionally known.

It will be understood that while the type of pump illustrated in the aforesaid Jennings patent, No. 2,0'73,014 has'been described herein as an adapation of a liquid pump which might be used in the combination, that this description is not intended as limiting, as various other turbine or Further, practically in all respects the combination of this liquid impeller with the gas pump figures is the same as the combination between the centrifugal pump impeller and the gas pump illustrated in the early described figures, the principal difference being in the characteristics of the liquid pump portion of the unit.

Similarly variations in the type of liquid ring pump are contemplated, as within the scope of the invention, the hereindescribed embodiments being primarily illustrative. While the gas pump illustrated herein is provided with conical port members, it is quite, obvious that many modifications will occur to those skilled in the art. For example, the liquid ring pump might be of the type which is provided with cylindrical port members, or with a side port member, as distinguished from a cone or a tapered port member.

From the foregoing,

' conventionally intended, but by the sealing principles applied, it extremely compact, serving, with a combined impeller,

is made possible to produce an highly emcient unit, prethe individual circulating impulse action of the pump of the impulse type, as well the operation of the various embodiments of the invention herein shown The gas pump portion will func-.

what I claim as new and desire to acts as the main dividing wall or partition between the two pumps, the normal running clearance between said moving partition wall and the pump housing .being cared for by the several seals.

Also, it is obvious that regardless of the types of pump which are utilized, the principles of the invention may be applied even if the impellers are separated, just as in the described embodiment of Figure 13.

Having thus fully described my ,invention,

Letters Patent of the United States is:

1. In aunitary centrifugal liquid pump and liquid ring gas compressor including a casing, a common unitary impeller-therein adapted to handle liquid at one side of the pump-compressor and gas at another side of the pump-compressor, and means for creating and maintaining a liquid seal between said liquid and gas sides, at

secure by.

a pressure essentially that of the pressure in the discharge of the gas side.

2. In a unitary centrifugal, liquid pump and liquid ring gas compressor, a common unit casing divided to provide regions for the handling of liquid and gas, means to pump liquid and compress gas therein, and means for creating and maintaining a liquid seal between said regions at a pressure essentially that of the pressure in the discharge of the gas region.

3. In a unitary liquid pump and gas compressor, a common unitary impeller adapted to handle liquid at one side of the pump-compressor and gas at the other side thereof, means for creating a liquid seal between said liquid and gas sides, and means to-maintain said seal at a pressure essentially that of the pressure inthe discharge of the gas side.

4. In a unitary liquid pump and liquid ring gas compressor, a common unit casing divided to provide regions for the handling of liquid and gas, means to pump liquid and compress gas therein, means to pump liquid and compress gas therein, including liquid ring displacement chambers cooperative with the liquid ring of the gas compressor, means for creating a liquid seal between said regions, and means for maintaining said seal at a pressure essentially that of the pressure in the discharge of the gas region.

5. In a unitary liquid pump and liquid ring gas compressor, acommon unit casing providing regions for the handling of liquid and gas. means in said casing to pump liquid in the liquid region, means also in said casing to compress gas in the gas region, including liquid ring displacement chambers cooperative with the liquid ring of the gas compressor, and means for creating and maintaining a liquid seal between said pumping and compressing means at a pressure essentially that of the pressure in the discharge of the gas region.

6. In a unitary liquid pump and liquid ring gas compressor, a common unit casing providing regions for the handling of liquid and gas, means in said casing to pump liquid in the liquid region, separate means also in said casing to compress gas in the gas region, including liquid ring displacement chambers cooperative with the liquid ring of the gas compressor, means, for creating a liquid seal between said pumping and compressing means, and means for maintaining said seal at a pressure essentially that of the pressure in the discharge of the gas region,

' means for creating and maintaining liquid side of the taining a liquid 7. In a unitary impulse type liquid pump and liquid ring. as compressor, a common unitary impeller adapted to handle liquid at one side of the pump compressor and gas at another side thereof, means including sealing surfaces on the impeller for creating and mainseal between said liquid and gas sides at a pressure essentially that of the pressure in the discharge of the gas side.

8. In a unitary centrifugal liquid pump and liquid ring gas compressor including a casing, a common unitary impeller therein adapted to handle liquid at one side of the pump-compressor, and gas at another side of the pump-compressor, and meansfor creating and maintaining a liquid seal between said liquid and gas sides at, a desired intermediate pressure. between that of the pressure in the discharge region of the liquid pump and that of the pressure in the discharge region of the gas compressor.

9. In a unitary centrifugal pump and liquid ring gas compressor including a casing, a common unitary impeller therein adapted to handle liquid at one side of the pump-compressor, and gas at another side of the pump-compressor, a liquid seal between said liquid and gas sides, at a desired intermediate pressure between that of the pressure in the discharge region of the liquid pump and that of the pressure in the dischargeregion of the gas compressor, and for creating and maintaining a liquid seal between said liquid and gas sides, at a pressure essentially that of the pressure in the discharge of the gas side.

10. In a unitary centrifugal pump and liquid ring gas compressor, a common unit casing divided to provide regions for the handling of liquid and gas, means to pump liquid and compress gas therein, means for creating and maintaining a liquid seal between said regions at a desired intermediate pressure between that of the pressure in the discharge region of the liquid pump and that of the pressure in the discharge region of the gas compressor, and for creating and maintaining a liquid seal between said regions at a pressure essentially that of the pressure in the discharge of the gas region.

. 11. In a. unitary liquid gas compressor, a common unitary impeller adapted to handle liquid at one side of the pumpcompressor and gas at the other side thereof, means for creating a liquid seal between said liquid and gas sides, and means to maintain said seal at a desired intermediate pressure between that oi. the pressure in the discharge region of the liquid pump and that of the pressure in the discharge region of the gas compressor.

12. In a unitary impulse type liquid pump and liquid ring, gas compressor, a common unitary impeller adapted to handle liquid at one side of the pump compressor and gas at another side thereof, means including sealing surfaces on the liquid side of the impeller for creating and maintaining a liquid seal between said liquid and gas sides at a desired intermediate pressure between that of the'pressure in the discharge region of the liquid. pump and that of the pressure in the discharge region of the gas compressor, and for maintaining a part of said seal at a pressure essentially that of the pressure in the discharge of the 88s side.

13. In a unitary centrifugal liquid pump and liquid ring gas compressor including a casing, a common unitary impeller therein adapted to pump and liquid ring liquid ring gas. compressor, a common handle liquid at one side of the pump-compressor, and gas at another side of the pump-compressor, a seal chamber between said liquid and gas sides, and means for creating and maintaining a liquid seal in said chamber at a pressure essentially that of the pressure in thedischarge of the gas side.

14. In a unitary centrifugal liquid pump and liquid ring gas compressor including a casing, a common unitary impeller therein adapted to handle liquid at one side of the pump-compressor, and gas at another side of the pump-compressor, a seal chamber between said liquid and gas sides, and means for creating and maintaining a liquid seal in said chamber at a desired intermediate pressure between that of the pressure in the discharge region of the liquid pump and that of the pressure in the discharge region of the gas compressor.

15. In a unitary centrifugal liquid pump and liquid ring gas compressor, a common unit casing divided to provide regions for the handling of liquid and gas, means to pump liquid and compress gas therein, a seal chamber between said liquid and gas regions, and means for creating and maintaining a liquid seal in said chamber at a pressure essentially that of the pressure in the discharge of the gas region.

16. In a unitary centrifugal liquid pump and liquid ring gas compressor, a common unit casing divided to provide regions for the handling of liquid and gas, means to pump liquid and compress gas therein, a chamber between said liquid and gas regions, and means for creating and maintaining a liquid seal in said chamber, at a desired intermediate pressure between that of the pressure inthe discharge region of the liquid pump and that of the pressure in the discharge region of the gas compressor.

1'7. In a unitary liquid pump and gas compressor, a common unitary impeller adapted to handle liquid at one side of the pump-compressor and gas at the other side thereof, a chamber between said liquid and gas sides, means for creating a liquid seal insaid chamber, and means to maintain said seal at a pressure essentially thatof the pressure in the discharge of the gas side.

liquid ring gas compressor, a common unitary impeller adapted to handle liquid at one side of the pump-compressor and'gas at another side thereof, means including sealing surfaces-on the liquid side of the impeller and sealing surfaces on the interior of the casing for forming a seal chamber, and means to create and maintain a liquid seal in said chamber at a pressure essentially that of the pressure in the discharge of the gas side.

18. In a unitary impulse type liquid pumpand T 7 5o pump and compress gas therethrough by the displacing action,of these blades cooperating impeller adapted to handle liquid at one side of the pump-compressor and gas at another side thereof, means includingsealing surfaces on the liquid side of the impeller and sealing surfaces on the interior of the casing for forming a seal chamber, and means to create and maintain a liquid seal in said chamber at a desired intermediate pressure.

20. In a unitary centrifugal pump and liquid 10 ring gas compressor, a common unit casing divided to provide regions for the handling of liquid and gas, means to pump liquid and compress gas therein, a plurality of seal chambers between said liquid and gas regions, means for creating and maintaining a liquid seal in one of said chambers at a pressure essentially that of the pressure in the discharge of the gas region and for creating and maintaining a liquid seal in-another of said chambers at a desired intermediate pressure between that of the pressure in the discharge region of the liquid pump and that of the pressure in the discharge region of the gas compressor.

21. A pump comprising a pump casing provided with a compartment including a rotating disc or partition wall traversing the compartment and dividing said compartment into separate pump chambers, said disc having typical centrifugal pump blades on one side and extending'into one of these pump chambers to operate as a typical centrifugal liquid pump and having onthe opposite side of said disc forward curved rotor blades forming rotating displacement buckets which operate in the other pump chamber to pump and compress gas therethrough by the displacing action of these blades cooperating with a liquid ring operating eccentricaily in said other pump chamber.

22'. A pump comprising a pump casing provided with a compartment including a rotating disc or partition wall traversing the compartment and dividing said compartment into separate pump chambers, said disc having typical centrifugal pump blades on one side and extending into one of these pump chambers to operate as a typical centrifugal liquid pump and having on the opposite side of said disc forward curved rotor blades forming rotating displacement buckets which operate in the other pump chamber to the minor axis'of the ellipseand with suitably placed cooperating inlet and outlet ports for the, pumping and compression of gas therethrough by the displacing action of the elliptical 'casing on the circulated liquid ring.

-19.- m a unitary impulse type liquid pum e s o0 HAROLD a. some.

unitary 

